Rapidly retractable tool support for a pipe machining apparatus

ABSTRACT

Pipe machining apparatuses, tool supports, and methods of operating pipe machining apparatuses are provided. In one aspect, a pipe machining apparatus includes a frame, a tool carrier coupled to and movable relative to the frame, and a tool support coupled to and movable with the tool carrier relative to the frame. The tool support is adapted to support a tool and move the tool in a first direction toward a pipe at a first increment and move the tool in a second direction away from the pipe at a second increment. The second increment is larger than the first increment.

RELATED APPLICATIONS

The present application is a continuation of co-pending U.S.Non-Provisional patent application Ser. No. 13/796,277, filed Mar. 12,2013, which claims the benefit of U.S. Provisional Patent ApplicationNo. 61/709,514, filed Oct. 4, 2012, the entire contents of all of whichare incorporated by reference herein.

FIELD OF THE INVENTION

The present disclosure generally relates to pipe machining apparatusesand, more particularly, to pipe machining apparatuses for machininglarge diameter pipes.

BACKGROUND

A variety of different types of pipe machining apparatuses exist toperform various machining processes on pipes. One such process includescutting pipes. Large diameter pipes may be cut with a split frame pipemachining apparatus, which includes two frame halves that surround thepipe from respective sides and are coupled together around the pipe.Such a pipe cutter includes a tool or cutting device that encircles thepipe and moves toward the pipe in small increments during the cuttingprocess in order to slowly cut into the pipe. Eventually, after manysmall increments of adjustment toward the pipe, the pipe will becompletely cut.

After completion of the cutting process, the cutting device must beretracted from its advanced cutting position. Due to the smallincrements of adjustment that are made to move the cutting device to itsadvanced cutting position, retraction of the cutting device is also madein small increments. This retraction of the cutting device is a verytime consuming process.

It would therefore be desirable to retract the cutting device from theadvanced cutting position in a manner requiring less effort and lesstime.

SUMMARY

The present disclosure is defined by the following claims, and nothingin this section should be taken as a limitation on those claims.

In one aspect, a pipe machining apparatus is provided and includes aframe, a tool carrier coupled to and movable relative to the frame, anda tool support coupled to and movable with the tool carrier relative tothe frame. The tool support is adapted to support a tool and move thetool in a first direction toward a pipe at a first increment and movethe tool in a second direction away from the pipe at a second incrementwith the second increment larger than the first increment.

In another aspect, a method of operating a pipe machining apparatus isprovided. The method includes fixedly coupling a frame of the pipemachining apparatus to a pipe, moving a tool carrier relative to theframe with the tool carrier being coupled to the frame, advancing a toolcoupled to the tool carrier toward the pipe at a first increment, andretracting the tool away from the pipe at a second increment larger thanthe first increment.

In a further aspect, a tool support for a pipe machining apparatus isprovided. The tool support includes a rotatable feed screw and a toolclamp coupled to the feed screw and adapted to support a tool. The toolclamp is movable along the feed screw to move the tool in a first tooldirection and a second tool direction. The tool support also includes aworm gear movable between a first position, in which the worm gearcouples with the feed screw and rotation of the worm gear in a firstworm gear direction rotates the feed screw to move the tool in the firsttool direction and rotation of the worm gear in a second worm geardirection rotates the feed screw to move the tool in the second tooldirection, and a second position, in which the worm gear is uncoupledfrom the feed screw and the feed screw is rotatable independently of theworm gear.

BRIEF DESCRIPTION OF THE DRAWINGS

The disclosure can be better understood with reference to the followingdrawings and description. The components in the figures are notnecessarily to scale, emphasis instead being placed upon illustratingthe principles of the disclosure.

FIG. 1 is a top front perspective view of an exemplary pipe machiningapparatus coupled to a pipe, in accordance with one embodiment.

FIG. 2 is a bottom rear perspective view of the pipe machining apparatusillustrated in FIG. 1, in accordance with one embodiment.

FIG. 3 is a front view of the pipe machining apparatus illustrated inFIG. 1 with a portion thereof broken away to show internal components ofthe pipe machining apparatus, in accordance with one embodiment.

FIG. 4 is an enlarged front view of an exemplary tool support of thepipe machining apparatus shown in FIG. 1 with the tool supportillustrated in an engaged position, in accordance with one embodiment.

FIG. 5 is an exploded view of the tool support of the pipe machiningapparatus shown in FIG. 4, in accordance with one embodiment.

FIG. 6 is a perspective view of an exemplary worm gear assembly and anexemplary drive coupling of the pipe machining apparatus shown in FIG.4, in accordance with one embodiment.

FIG. 7 is a cross-sectional view taken along line 7-7 in FIG. 4 showingthe tool support of the pipe machining apparatus in an engaged position,in accordance with one embodiment.

FIG. 8 is an enlarged front view of the tool support of the pipemachining apparatus shown in FIG. 1 with the tool support illustrated ina disengaged position, in accordance with one embodiment.

FIG. 9 is a cross-sectional view taken along line 9-9 in FIG. 8 showingthe tool support of the pipe machining apparatus in a disengagedposition, in accordance with one embodiment.

DETAILED DESCRIPTION

Methods and devices consistent with the present disclosure overcome thedisadvantages of conventional pipe machining apparatuses by providing,among other things, a tool support that can rapidly retract a tool uponcompletion of machining a pipe.

With reference to FIGS. 1-3, there is shown one exemplary embodiment ofa pipe machining apparatus 20 adapted to machine pipes P of varyingdiameters. In some exemplary embodiments, the apparatus 20 completelycuts through pipes P. In other exemplary embodiments, the apparatus 20prepares an end of a pipe P for coupling to another pipe. In still otherexemplary embodiments, the apparatus 20 both completely cuts andprepares a pipe P for coupling to another pipe.

In the illustrated exemplary embodiment, pipe machining apparatus 20 isformed of two joined-together semicircular sections 24A, 24B andincludes a frame 28 and a tool carrier 32. The two sections 24A, 24Btogether comprise the frame 28 and the tool carrier 32 such that a firstportion of the frame 28 and a first portion of the tool carrier 32 isincluded in one section 24A and a second portion of the frame 28 and asecond portion of the tool carrier 32 is included in the other section24B. The frame 28 has a column 36 extending outwardly of the twosemicircular sections 24A, 24B and houses a pinion gear 40 adapted tocouple with a suitable drive motor 44, such as an air motor withsuitable gear reduction means. The frame 28 is adapted to couple and befixed relative to a pipe P, and the tool carrier 32 is rotatablerelative to the fixed frame 28 and the pipe P. The air motor 44 isadapted to rotate the tool carrier 32 relative to the frame 28 through agear train in the column 36. The tool carrier 32 has a circular gearrack 56 for meshing with the pinion gear 40 rotatably mounted in column36. The pinion gear 40 has an opening 60 provided with a polygonalperimeter for receiving a complementary shaped drive head 64 of drivemotor 44. Therefore, it can be seen that drive motor 44 is adapted torotate tool carrier 32 relative to the frame 28 through a gear trainprovided by pinion gear 40 in column 36 and circular gear rack 56 on thetool carrier 32.

The rotatable tool carrier 32 includes one or more tool supports 48 (twotool supports shown in the illustrated exemplary embodiment), whichsupport tools 52 for performing a cutting or machining operation on thepipe P as the tools 52 rotate circumferentially about the pipe P. Themachining operation performed by the tool(s) 52 may form a straight edgeperpendicular to a longitudinal extent of the pipe P, a bevel on an endof the pipe P that is transverse to the longitudinal extend of the pipeP and at an angle other than ninety degrees, or an edge of a pipe Phaving any angle.

The apparatus 20 further includes four adjustable clamp members orcoupling members 68 engageable with an exterior of the pipe P and havingsuitable adjustability to couple and concentrically locate the apparatus20 to the pipe P.

As best seen in FIG. 3, tool carrier 32 is rotatably mounted on andsupported by frame 28 by a plurality of roller bearings 72. The rollerbearings 72 ride in a circular bearing race 76 on the interior of toolcarrier 32.

A plurality of projections 80 are adjustably movable into and out of apath of an advancement member 84 coupled to each tool support 48 toadvance the tool 52 toward the pipe P. In the illustrated exemplaryembodiment, the apparatus 20 includes a total of two projections 80 forengaging the advancement members 84, however, the apparatus 20 mayinclude any number of projections 80. Each projection 80 is coupled to alever 88 that may be actuated by a user to selectively move theprojection 80 into and out of the path of the advancement members 84.

With continued reference to FIGS. 1 and 3, and further reference toFIGS. 4-7, a tool support 48 of the tool carrier 32 is illustrated inmore detail. The tool support 48 includes a base 92, a feed screw 96rotatably coupled to the base 92, a tool clamp 100 adapted to support atool 52 and movable along the feed screw 96, a worm gear housing 104coupled to the base 92, a worm gear assembly 108 supported by and atleast partially positioned within the worm gear housing 104, a drivecoupling 112 engageable with the worm gear assembly 108, and theadvancement member 84 coupled to the drive coupling 112.

The tool support 48 is coupled to the tool carrier 32 by one or morecoupling members 116 (two shown in the exemplary illustrated embodiment)and is adjustable relative to the pipe P to bring an arcuate edge 120 ofthe base 92 into contact with or in close proximity to an outerperiphery of the pipe P. The tool clamp 100 is adapted to support a tool52 and is movable along the feed screw 96 toward and away from the pipeP (depending on the direction of feed screw rotation). The feed screw 96can have a variety of different tooth shapes, sizes, pitches, andconfigurations in order to provide a desired amount of tool movementduring use of the apparatus 20. A drive gear 124 is coupled to the feedscrew 96 and is engageable with the worm gear assembly 108 to transferrotation of the worm gear assembly 108 to the feed screw 96. A toolcoupling 128 such as, for example, a nut, is coupled to an end of thefeed screw 96, thereby providing a location where a tool may couple toand rotate the feed screw 96 as desired.

The worm gear housing 104 defines a cavity 132 therein for receiving atleast a portion of the worm gear assembly 108, the drive coupling 112,and the advancement member 84. The worm gear assembly 108 includes ashaft 136, a knob 140, a set screw 144, a housing 148, a first washer152, a urethane washer 154, two thrust bearings 156, two bushings 160, aworm gear 164, and a key element 168. The worm gear 164 is fixed to theshaft 136 and, in some embodiments, the worm gear 164 may be unitarilyformed as one-piece with the shaft 136. The worm gear 164 is coupled orinterlaced with the drive gear 124, thereby causing the feed screw 96 torotate when the worm gear assembly 108 rotates. The knob 140 is coupledto one end of the shaft 136 and the key element 168 is defined in asecond end of the shaft 136. The key element 168 is adapted to engagewith a similarly configured key feature 172 in the drive coupling 112,which is coupled to the advancement member 84. The key element 168 andcomplementary key feature 172 in the drive coupling 112 may have a widevariety of configurations. In the illustrated exemplary embodiment, thekey element 168 includes a pair of projections 176 extending from an endsurface of the worm gear 164. One projection 176 extends from the endsurface on one side of the shaft 136 and a second projection 176 extendsfrom the end surface on an opposite side of the shaft 136. The keyfeature 172 in the drive coupling 112 is comprised of a complementaryshaped slot defined in an end of the drive coupling 112. The slot 172 isadapted to receive the key element 168 in an appropriate orientation andcause the worm gear assembly 108 and the drive coupling 112 to rotatetogether. In this manner, rotation of the advancement member 84 causesthe worm gear assembly 108 to rotate.

Tool support 48 further includes rollers 180 engageable with a flange184 of the worm gear assembly housing 148 and springs 188 engaging andapplying constant force to the rollers 180. A pair of keeper plates 192are coupled to the worm gear housing 104 to secure the rollers 180 andsprings 188 in place, and each keeper plate 192 defines an aperture inwhich the associated roller 180 is positioned and retained. The wormgear assembly housing 148 is adapted to engage and roll over the rollers180, with the rollers 180 applying a force to the flange 184. The flange184 includes a pair of indentations 194 therein for receiving therollers 180 when the worm gear assembly 108 is in the engaged position.

During operation of the apparatus 20, the motor 44 rotates the piniongear 40, which, through engagement with the gear rack 56, causes thetool carrier 32 to rotate relative to the frame 28 and the pipe P.During tool carrier rotation, the advancement member 84 contacts theadvancement projections 80 and rotates as a result, thereby rotating theworm gear assembly 108 due to the engagement between the key element 168and key feature 172. Rotation of the worm gear 164 causes the drive gear124 to rotate, which rotates the feed screw 96 to ultimately move thetool clamp 100 and tool 52 toward the pipe P to perform deeper machininginto the pipe P. The tool 52 advances until the pipe P is machined to adesired extent (e.g., until the pipe is completely cut or parted).

After the desired amount of machining is achieved, it may be desirableto retract the tool 52 along the tool support 48 from the advancedcutting position. Tool retraction can be achieved in a couple manners.First, the knob 140 may be turned in an opposite direction to that foradvancing the tool 52, thereby causing the worm gear assembly 108 torotate in an opposite direction and also rotate the feed screw 96 in anopposite direction. The tool 52 and tool clamp 100 retract or move awayfrom the pipe P when the feed screw 96 is rotated in the oppositedirection. Due to the large ratio of the worm gear 164 and the drivegear 124, each complete rotation of the worm gear 96 assembly onlyretracts the tool 52 a small increment. Thus, many turns of the wormgear assembly 108 are required to retract the tool 52 a large amount.Retraction of the tool 52 in this manner can include a lot of effort andis time consuming With the worm gear 164 and drive gear 124 engaged inthe manner illustrated in FIG. 7, it is not possible to engage the toolcoupling 128 on the feed screw 96 with a tool and rotate the feed screw96 in the opposite direction without damaging the worm gear assembly 108and/or the drive gear 124.

A second manner of retracting the tool 52 after completion of the pipemachining process exists. This second manner includes moving the wormgear assembly 108 from an engaged position (as shown in FIGS. 4 and 7)to a disengaged position (as shown in FIGS. 8 and 9). With reference toFIGS. 8 and 9, the disengaged position of the worm gear assembly 108 isillustrated and includes moving the worm gear 164 out of engagement withthe drive gear 124. To achieve this, a user grasps and twists the flange184 on the worm gear assembly housing 148 causing the flange 184 to rollalong the top of the rollers 180. A first slot 196 defined in the wormgear assembly housing 148 rotates until an inner edge of at least one ofthe keeper plates 192 is no longer positioned in the first slot 196.Once the keeper plate 192 is no longer positioned in the first slot 196,the worm gear assembly 108 may be pulled upward to the disengagedposition shown in FIG. 9. Pulling the worm gear assembly 108 upwarddisengages the worm gear 164 with the drive gear 124. A second slot 200is defined in the worm gear assembly housing 148 and the worm gearassembly 108 may be rotated to move at least one of the keeper plates192 into the second slot 200 to retain the worm gear assembly 108 in thedisengaged position. FIGS. 4 and 8 include reference lines 204 on theflange 184 of the worm gear assembly housing 148 to illustrate theorientation of the worm gear assembly 108 in the engaged and disengagedpositions and the necessary rotation of the flange 184 to move theassembly 108 between the engaged and disengaged positions.

Upon disengagement of the worm gear 164 with the drive gear 124, thefeed screw 96 may be rotated in an opposite direction to retract thetool clamp 100 and the tool 52. A rotary tool (e.g., a power drill) mayengage the tool coupling 128 to rotate the feed screw 96 in the oppositedirection. Since the drive gear 124 no longer engages the worm gear 164,rotation of the feed screw 96 in the opposite direction will not damagethe drive gear 124 or the worm gear 164. Additionally, the large ratiobetween the worm gear 164 and the drive gear 124 is taken out of play bydisengaging the worm gear 164 and the drive gear 124. Thus, the tool 52and the tool clamp 100 may be retracted at an increment associated withthe teeth configuration of the feed screw 96. This increment issignificantly larger than the small increment associated with the largegear ratio between the worm gear 164 and the drive gear 124, therebyensuring quicker retraction of the tool 52 and the tool clamp 100.

The worm gear assembly 108 may be moved back into the engaged positionas desired. To achieve this, the housing 148 of the worm gear assembly108 is rotated to move the keeper plate 192 out of the second slot 200and the worm gear assembly 108 is then moved into the cavity 132 towardthe drive coupling 112. The worm gear 164 interlaces with the teeth ofthe drive gear 124 and the worm gear assembly 108 is rotated until thekey element 168 is positioned in the key feature 172 defined in thedrive coupling 112. When the key element 168 moves into the key feature172, a user presses the flange 184 against the rollers 180 andassociated spring force to align the first slot 196 with at least one ofthe keeper plates 192. The worm gear assembly 108 is then rotated toslide at least one of the keeper plates 192 into the first slot 196 andthe rollers 180 seat themselves into the indentations 194 defined in theflange 184. At this point, the worm gear assembly 108 is located in theengaged position and the tool carrier 32 is ready for use.

The Abstract of the disclosure is provided to allow the reader toquickly ascertain the nature of the technical disclosure. It issubmitted with the understanding that it will not be used to interpretor limit the scope or meaning of the claims. In addition, in theforegoing Detailed Description, it can be seen that various features aregrouped together in various embodiments for the purpose of streamliningthe disclosure. This method of disclosure is not to be interpreted asreflecting an intention that the claimed embodiments require morefeatures than are expressly recited in each claim. Rather, as thefollowing claims reflect, inventive subject matter lies in less than allfeatures of a single disclosed embodiment. Thus, the following claimsare hereby incorporated into the Detailed Description, with each claimstanding on its own as a separately claimed subject matter.

While various embodiments of the disclosure have been described, it willbe apparent to those of ordinary skill in the art that other embodimentsand implementations are possible within the scope of the disclosure.Accordingly, the disclosure is not to be restricted except in light ofthe attached claims and their equivalents.

1. A pipe machining apparatus comprising: a frame; a tool carriercoupled to and movable relative to the frame; and a tool support coupledto and movable with the tool carrier relative to the frame, wherein thetool support is adapted to support a tool and move the tool in a firstdirection toward a pipe at a first increment and move the tool in asecond direction away from the pipe at a second increment, the secondincrement being larger than the first increment.
 2. The pipe machiningapparatus of claim 1, wherein the first increment is a first lineardistance traveled per a period of time and the second increment is asecond linear distance traveled per the same period of time, wherein thesecond linear distance is greater than the first linear distance.
 3. Thepipe machining apparatus of claim 1, wherein the tool support is adaptedto move the tool in the second direction at the first increment and thesecond increment.
 4. The pipe machining apparatus of claim 1, whereinthe tool support is adapted to move the tool in the first direction atthe first increment and the second increment.
 5. The pipe machiningapparatus of claim 1, wherein the tool support is adapted to move thetool in the first direction at the first increment and the secondincrement, and wherein the tool support is adapted to move the tool inthe second direction at the first increment and the second increment. 6.A tool support for a pipe machining apparatus, the tool supportcomprising: a rotatable feed screw; and a tool clamp coupled to the feedscrew and adapted to support a tool, wherein the tool clamp is movablealong the feed screw to move the tool in a first tool direction and asecond tool direction, and wherein the tool is moveable in the firsttool direction at a first increment and a second increment larger thanthe first increment, and wherein the tool is moveable in the second tooldirection at the first increment and the second increment.
 7. The toolsupport of claim 6, further comprising a worm gear movable between afirst position, in which the worm gear couples with the feed screw androtation of the worm gear in a first worm gear direction rotates thefeed screw to move the tool in the first tool direction and rotation ofthe worm gear in a second worm gear direction rotates the feed screw tomove the tool in the second tool direction, and a second position, inwhich the worm gear is uncoupled from the feed screw and the feed screwis rotatable independently of the worm gear.
 8. The tool support ofclaim 7, wherein the tool moves at the first increment in the firstdirection and the second direction with the worm gear coupled to thefeed screw, and wherein the tool moves at the second increment in thefirst direction and the second direction with the worm gear uncoupledfrom the feed screw.
 9. The tool support of claim 7, wherein a drivegear is fixedly coupled to and rotates with the feed screw, and whereinthe worm gear engages the drive gear in the first position and does notengage the drive gear in the second position.
 10. The tool support ofclaim 7, wherein the first increment is a first linear distance traveledby the tool as a result of a single rotation of the worm gear, andwherein the second increment is a second linear distance traveled by thetool as a result of a single rotation of the feed screw, the secondlinear distance being larger than the first linear distance.
 11. Thetool support of claim 7, further comprising a drive coupling including akey feature, and wherein the worm gear includes a key element adapted tocouple with the key feature of the drive coupling to couple the wormgear to the drive coupling with the worm gear in the first position, andwherein the worm gear and the drive coupling rotate together whencoupled.
 12. The tool support of claim 11, wherein the key element isuncoupled from the key feature when the worm gear is in the secondposition, and wherein the worm gear and drive coupling rotateindependently of each other when uncoupled.
 13. A method of operating apipe machining apparatus, the method comprising: fixedly coupling aframe of the pipe machining apparatus to a pipe; moving a tool carrierrelative to the frame, wherein the tool carrier is moveably coupled tothe frame; advancing a tool coupled to the tool carrier toward the pipeat a first increment; and retracting the tool away from the pipe at asecond increment larger than the first increment.
 14. The method ofclaim 13, wherein the first increment is a first linear distancetraveled per a period of time and the second increment is a secondlinear distance traveled per the same period of time, wherein the secondlinear distance is greater than the first linear distance.
 15. A methodof operating a tool support, the method comprising: providing a toolclamp adapted to support a tool; moving a worm gear to a first position;coupling the worm gear with a feed screw in the first position; rotatingthe worm gear in a first worm gear direction to rotate the feed screw;moving the tool clamp along the feed screw to move the tool in a firsttool direction upon rotating the worm gear in the first worm geardirection; rotating the worm gear in a second worm gear direction torotate the feed screw; moving the tool clamp along the feed screw tomove the tool in a second tool direction upon rotating the worm gear inthe second worm gear direction; moving the worm gear to a secondposition; uncoupling the worm gear from the feed screw in the secondposition; and rotating the feed screw independently of the worm gearwith the worm gear in the second position.
 16. The method of claim 15,further comprising: fixedly coupling a drive gear to the feed screw;rotating the drive gear with the feed screw; engaging the worm gear withthe drive gear in the first position; and disengaging the worm gear fromthe drive gear in the second position.
 17. The method of claim 15,further comprising: moving the tool at a first increment in the firstand second tool directions with the worm gear in the first position; andmoving the tool at a second increment in the second tool direction withthe worm gear in the second position, wherein the second increment islarger than the first increment.
 18. The method of claim 17, wherein thefirst increment is a first linear distance traveled by the tool as aresult of a single rotation of the worm gear, and wherein the secondincrement is a second linear distance traveled by the tool as a resultof a single rotation of the feed screw, the second linear distance beinglarger than the first linear distance.
 19. The method of claim 15,further comprising: coupling a key element of the worm gear with a keyfeature of a drive coupling with the worm gear in the first position;and rotating the worm gear and the drive coupling together when coupled.20. The method of claim 19, further comprising: uncoupling the keyelement from the key feature with the worm gear in the second position;and rotating the worm gear and the drive coupling independently of eachother when uncoupled.